EP3763981A1 - Screw joint for oil well pipe - Google Patents
Screw joint for oil well pipe Download PDFInfo
- Publication number
- EP3763981A1 EP3763981A1 EP19764512.0A EP19764512A EP3763981A1 EP 3763981 A1 EP3763981 A1 EP 3763981A1 EP 19764512 A EP19764512 A EP 19764512A EP 3763981 A1 EP3763981 A1 EP 3763981A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- screw
- joint
- pipe
- pin
- box
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000003129 oil well Substances 0.000 title claims abstract description 40
- 230000002093 peripheral effect Effects 0.000 claims abstract description 19
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 17
- 239000010959 steel Substances 0.000 claims abstract description 17
- 239000002184 metal Substances 0.000 claims abstract description 15
- 239000012530 fluid Substances 0.000 claims abstract description 7
- 238000010276 construction Methods 0.000 abstract description 14
- 238000012545 processing Methods 0.000 abstract description 12
- 238000013461 design Methods 0.000 description 10
- 238000012360 testing method Methods 0.000 description 8
- 238000004519 manufacturing process Methods 0.000 description 6
- 238000011156 evaluation Methods 0.000 description 5
- 230000000052 comparative effect Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000005457 optimization Methods 0.000 description 4
- 230000003014 reinforcing effect Effects 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 238000009412 basement excavation Methods 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 239000010779 crude oil Substances 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000002436 steel type Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/001—Screw-threaded joints; Forms of screw-threads for such joints with conical threads
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
- E21B17/02—Couplings; joints
- E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
- E21B17/042—Threaded
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/04—Screw-threaded joints; Forms of screw-threads for such joints with additional sealings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/06—Screw-threaded joints; Forms of screw-threads for such joints characterised by the shape of the screw-thread
Landscapes
- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Non-Disconnectible Joints And Screw-Threaded Joints (AREA)
Abstract
Description
- The present invention relates to screw joints for oil well pipes that connect oil well pipes including tubing and casing used for explorations or productions of oil wells or gas wells, and more particularly to screw joints for oil well pipes in which processing time and construction time are reduced.
- Screw joints are widely used for connecting steel pipes used in oil-producing industrial facilities such as oil well pipes. In the related art, standard screw joints for a pipe defined in American Petroleum Institute (API) standard are typically used for connections of the steel pipes used for explorations or productions of oil or gas.
- In recent years, since wells of crude oil or natural gas have been used in deep wells and horizontal wells, directional wells, or the like have been increased from vertical wells, excavation and production environments have been more severe. In addition, since development of wells in poor environments such as oceans and polar regions have been increased, required performance of screw joints for pipes such as compression resistance performance, bending resistance performance, or external pressure sealing performance have diversified. Because of such a required performance, use of high-performance special screw joints for pipes called premium joints have increased.
- In addition, in order to reduce the volume of excavation amount when wells are developed, it is necessary to make the wells slimmer. Therefore, among the premium joints, there is also growing demands for screw joints for pipes of integral types for directly connecting tubes (also referred to as pipes) without using coupling members.
- The premium joint usually has a taper screw and a metal touch seal portions on a pipe end side of each pipe. These portions are respective elements constituting a pin that is a male screw portion provided on one end side of the pipe and a box that is a female screw portion screwed or fitted to the male screw portion provided on one end side of the pipe. These elements are designed so that a male taper screw and a female taper screw, and a male metal touch seal portion and a female metal touch seal portion face each other when tightening a joint
- (screw joint for a pipe, the same is applied to the following description). Moreover, the taper screw is necessary to tightly fix the joint. The metal touch seal portion secures a sealing property using metal contact between the box and the pin in a region of the metal touch seal portion.
- In the screw joint for a pipe (hereinafter, also referred to as an integral joint) of the integral type, the metal touch seal portion is provided at one or two or more places in an axial direction (pipe axis direction, the same is applied to the following description) . The metal touch seal portion is provided at least at one place of an outer peripheral surface of a non-screw portion (hereinafter, referred to as a nose) connected to a screw end on a pin distal end side of the taper screw of the pin and an inner peripheral surface of a non-screw portion (hereinafter, referred to as a nose hole) connected to a screw end on a box rear end side of the taper screw of the box.
- As a prior technique of the related art of the integral joint, a screw joint 1 (pipe screw joint) for a pipe described in PTL 1 is illustrated in
Fig. 2 . An object of the invention described in PTL 1 is to produce a screw joint for a pipe, which maintains an appropriate rigidity and is provided with an improved seal, improve structural resistance (characteristic) of a joint against a high load, in particular, a compressive load, and cause the characteristics not to affect a sealing function. In the invention described in PTL 1, a reinforcing section protruding from the metal touch seal portion on a non-screw surface on the distal end side of thebox 3 to a most distal end of the box is provided, a length of the reinforcing section or further a wall thickness (thickness) thereof is defined, and an entire length of the reinforcing section of the box is not in contact with the corresponding pipe (raw pipe portion) on the rear end side of apin 2. - [PTL 1] Japanese Patent No.
5232475 - However, in the technique described in PTL 1, there is not mentioned about optimization of the screw length of the joint. There was room for improvement for the optimization of the screw length so as to achieve both productivity and shear fracture strength of the joint.
- Normally, in the oil well pipe, a plurality of pipes having joint portions (generally referred to as the male screw portion and the female screw portion) are connected in series with the joint portions and are inserted in the well. In this state, a relatively large tensile load acts on the joint portion as in the pipe closer to the ground surface. Therefore, it is required for the screw joint for an oil well pipe to have strength that can avoid shear fracture such as fatigue fracture and tensile fracture as one of important joint performances. As a method for securing the strength of the joint portion, it is required to provide the joint portion with a long screw length to a certain extent. In general, in order to have the strength at which the joint portion can avoid the shear fracture, it is necessary for the shear fracture strength of the screw portion to exceed the tensile fracture strength of the joint portion, and it is necessary to design shear stress of the screw portion to be 1/√3 times or less the tensile stress of the joint portion. Moreover, the screw length of the joint portion refers to an entire length of a portion where the male screw portion and the female screw portion in the joint portion are in a fitted state.
- However, in order to secure the shear fracture strength, making the screw length of the joint portion extremely long poses a problem that a processing time increases in proportion to the screw length when threading or rolling to the steel pipe (raw pipe). In addition, when the screw is tightened, there is also a problem that the construction time extension. This causes poor productivity and increase in manufacturing cost.
- In view of the above problems, an object of the present invention is to provide a screw joint for an oil well pipe in which optimization of a screw length of a joint portion is achieved, and a processing time and a construction time are reduced.
- The present inventors diligently studied in order to solve the above problems.
- As described above, since in the oil well pipe, the plurality of pipes are connected in series with the joint portions and are inserted in the well, a relatively larger tensile load acts on the joint portion as in the pipe closer to the ground. In the joint portion, breakage of the pin, breakage of the box, or the like may occur. Therefore, it is required that the joint portion has strength enough to avoid the shear fracture as one of important joint performances. In response to the requirement, in order to secure the strength, it is usually dealt with by designing the screw length of the joint portion to be longer. Therefore, in general, it is designed with an excessive increase in the screw length in view of (in consideration of) safety. Therefore, the present inventors focused attention on a design such that the screw portions (referred to as the male and female taper screw portions) of the joint portion have a minimum necessary screw length not to cause the shear fracture and diligently studied on a screw joint for an oil well pipe in which both productivity and the shear fracture strength of the joint can be achieved.
- As a result, it was found that the shear fracture of the screw portions can be prevented by defining a minimum necessary screw length Lmin (mm) such that a ratio of the shear stress acting on the male and female taper screws to the tensile stress acting on the critical cross-section of the joint when a tensile stress is applied to the joint is equal to or less than a predetermined value.
- The present invention has been made based on the above-described findings and the gist thereof is summarized as follows.
- [1] A screw joint for an oil well pipe of an integral type, including: a pin that is provided with a male screw portion which is a male taper screw, at one end of a steel pipe; and a box that is provided with a female screw portion which is a female taper screw fitted to the male screw portion, at one end of the steel pipe,
in which a structure, in which the pin and the box are in metal contact with each other to seal a fluid, is provided at least at one place of a seal portion on an outer peripheral surface side of a pipe end side of the pin and a seal portion on an inner peripheral surface side of a pipe end side of the box,
in which a minimum value Lmin (mm) of a screw length L (mm) in screw rows of the male taper screw and the female taper screw is defined by expression (1),
in which the screw length L (mm) in the screw rows satisfies expression (2).- Here, t: a pipe thickness (mm) of each of raw pipe portions which are unprocessed portions of the box and the pin,
- D: a pipe diameter (mm) of each of the raw pipe portions which are the unprocessed portions of the box and the pin,
- αt: a ratio of an effective screw length to the screw length L, a shorter effective screw length of the box or the pin being chosen for the effective screw length,
- Dt: an average screw diameter (mm) of screw valleys in the taper screw having a shorter effective screw length of the box or the pin, and
- joint efficiency: tensile strength of the joint portion/tensile strength of the raw pipe portion.
- Moreover, in the present invention, a minimum necessary screw length (Lmin (mm)) refers to a minimum value (lower limit value) of the screw length of the joint portion required for design, so that the screw portion has a strength that can avoid shear fracture.
- In addition, the screw length (L (mm)) of the joint portion refers to a length (that is, a screw length in the screw rows of the male taper screw and the female taper screw) of a portion (screw fitting portion) where the male screw portion and the female screw portion of the joint portion are meshed with each other when the joint portion is screwed and tightened.
- In addition, the effective screw length is a sum of lengths in an axial direction with respect to portions obtained by totaling bottom widths of screw threads of either the male screw portion or the female screw portion in the screw fitting portion, and is calculated for each of the male screw portion and the female screw portion.
- In addition, the ratio (αt) of the effective screw length is a ratio of the effective screw length to the screw length L and a shorter effective screw length of the box or the pin is chosen for the effective screw length.
- According to the present invention, it is possible to obtain a screw joint for an oil well pipe in which optimization of the screw length of the joint portion is achieved, and a processing time and a construction time are reduced.
-
-
Fig. 1 is a sectional view of a screw joint for an oil well pipe in a pipe axis direction for explaining an example of an embodiment of the present invention and a sectional view illustrating a portion where a pin and a box are tightened. -
Fig. 2 is a sectional view illustrating an example of a screw joint for an oil well pipe of the related art in a pipe axis direction. - Hereinafter, a screw joint 1 for an oil well pipe of the present invention will be described with reference to
Fig. 1 . Moreover, the present invention is not limited to the following embodiment.Fig. 1 is a sectional view of the screw joint 1 for the oil well pipe in a pipe axis direction for explaining an embodiment of the present invention and a sectional view illustrating a portion where apin 2 and abox 3 are tightened (fitted) and a periphery thereof. Moreover,Fig. 1 is also an explanatory view of expression (1) and expression (2) described below. - The screw joint 1 for the oil well pipe of the present invention includes the
pin 2 that is provided with a male screw portion 4 which is a male taper screw at one end of a steel pipe and thebox 3 that is provided with a female screw portion 5 which is a female taper screw fitted to the male screw portion 4 at one end of the steel pipe. In addition, the screw joint 1 for the oil well pipe of an integral type includes a structure, in which thepin 2 and thebox 3 are in metal contact with each other to seal a fluid, provided at least at one place of a seal portion 9 on an outer peripheral surface side of a pipe end side of thepin 2 and aseal portion 10 on an inner peripheral surface side of a pipe end side of thebox 3. A minimum value Lmin (mm) of a screw length L (mm) in screw rows of male and female taper screws is defined by the expression (1) described below and the screw length L (mm) in the screw rows satisfies the expression (2) described below. - First, a configuration of the screw joint 1 for the oil well pipe of the present invention will be described.
- As illustrated in
Fig. 1 , the screw joint 1 for the oil well pipe of the present invention connects the steel pipes with thepin 2 and thebox 3. The screw joint 1 for the oil well pipe is a screw joint (premium joint) in which thepin 2 and thebox 3 are coupled. In addition, the screw joint 1 for the oil well pipe is a screw joint of an integral type in which the steel pipes are directly connected by thepin 2 and thebox 3. - The
pin 2 is provided with the male screw portion 4 which is the male taper screw at one end of the steel pipe. Thebox 3 is provided with the female screw portion 5 which is the female taper screw fitted or screwed to the male screw portion 4 at one end of the steel pipe. Moreover, in the present invention, as illustrated inFig. 1 , a region including the male screw portion 4 and a periphery of anose 15 on a male side which is described below is referred to as thepin 2. A region including the female screw portion 5 and a periphery of a nose hole 16 on a female side which is described later is referred to as thebox 3. - The screw joint 1 for the oil well pipe has a structure in which the
pin 2 and thebox 3 are in metal contact with each other to seal a fluid. In a case of the screw joint 1 for the oil well pipe illustrated inFig. 1 , the seal structure is provided at two places of the seal portion 9 on an outer peripheral surface side of a pipe end side (positive direction side of an X-axis parallel to a screw joint axis α inFig. 1 ) of the male screw portion 4, and theseal portion 10 on an inner peripheral surface side of an pipe end side (negative direction side of the X-axis inFig. 1 ) of the female screw portion 5. - For example, when the joint is tightened, metal touch seal portions of the nose 15 (non-screw portion connected to a screw end of a distal end side of the pin 2) and the nose hole 16 (non-screw portion connected to a screw end on a far end side of the box 3) are in contact with each other, so that the seal portion 9 on the outer peripheral surface side forms a seal surface for preventing the fluid inside the pipe from entering the region of the taper screw.
- The
seal portion 10 on the inner peripheral surface side is provided on an outer peripheral surface (for the sake of convenience, referred to as a non-screw surface on the far end side of the pin) of the non-screw portion connected to the screw end on a far end side of thepin 2, and an inner peripheral surface (for the sake of convenience, referred to as a non-screw surface on the distal end side of the box) of the non-screw portion connected to the screw end of the distal end side of thebox 3. When the screw joint is tightened, the seal portions of the non-screw surface on the far end side of the pin and the non-screw surface on the distal end side of the box are in contact with each other, so that theseal portion 10 on the inner peripheral surface side forms a seal surface for preventing the fluid outside the pipe from entering the region of the taper screw. - In addition, the screw joint 1 for the oil well pipe may have a
shoulder portion 11 at a distal end of thepin 2. In this case, as illustrated inFig. 1 , ashoulder portion 12 abutting against theshoulder portion 11 on apin 2 side is also provided in thebox 3. - Moreover, the raw pipe portions refer to a region (unprocessed portion 7 of the box) of a pipe body other than the female screw portion 5 in the
box 3, and a region (unprocessed portion 6 of the pin) of the pipe body other than the male screw portion 4 in thepin 2, respectively. Both theunprocessed portion 6 of thepin 2 and the unprocessed portion 7 of thebox 3 are cylindrical shape. - Next, a relationship between the screw length L (mm) and the minimum value Lmin (mm) of the screw length in a
screw row 17 of the screw joint 1 for the oil well pipe of the present invention will be described with reference toFig. 1 . - It is important that the screw joint 1 for the oil well pipe of the present invention is designed so that the screw portions (referring to male and female taper screw portions) of the joint portion have a joint strength that is not subjected to shear fracture and a minimum necessary screw length to satisfy the tensile strength. Therefore, in the present invention, the allowable range of the screw length is determined as follows from a viewpoint of strength and dimensional restrictions.
- A lower limit value, that is, the minimum value Lmin (mm) of the screw length L (mm) in the
screw rows 17 of the male and the female taper screws is defined by the following expression (1). Furthermore, the screw length L (mm) in thescrew row 17 is necessary to satisfy the following expression (2) . - Here, t: a pipe thickness (mm) of the raw pipes of the unprocessed portions of the box and the pin,
- D: a pipe diameter (mm) of the raw pipes of the unprocessed portions of the box and the pin,
- αt: a ratio of an effective screw length to the screw length L, a shorter effective screw length of the box or the pin being chosen for the effective screw length,
- Dt: an average screw diameter (mm) of screw valleys in the taper screw having a shorter effective screw length of the box or the pin, and
- joint efficiency: tensile strength of the joint portion/tensile strength of the raw pipe portion.
- αt is determined by a design of a screw shape. In a case where a width of a screw bottom is different between the pin and the box, the effective length becomes shorter in the shape as a width of the screw bottom is narrower. In case of a design in which the width of a bottom portion of the screw thread is larger by comparing a width of a top portion and the width of the bottom portion, for example, in a trapezoidal screw, αt tends to be larger. Conversely, in a design in which the width of the bottom portion is smaller by comparing the width of the top portion and the width of the bottom portion of the screw thread, for example, in a wedge screw, αt tends to be smaller.
- In a case where the screw length L (mm) does not satisfy (Lmin × 1.0 ≤ L) of the expression (2), the screw portion may be subjected to the shear fracture by a tensile load equal to or less than the tensile strength of the joint in the pipe axis direction. Preferably, it is Lmin × 1.25 ≤ L. On the other hand, in a case where the screw length L (mm) does not satisfy (L ≤ Lmin × 2.5) of the expression (2), it cannot be said that the screw length is designed to be sufficiently short and it cannot be said that the screw joint is excellent in workability and productivity which are the effects of the present invention. Preferably, it is L ≤ Lmin × 2.0.
- Moreover, for example, in a case of the screw joint 1 for the oil well pipe illustrated in
Fig. 1 , thescrew row 17 refers to a region of the taper screw which is provided in each of thepin 2 and thebox 3. - In addition, as described below, the screw length L (mm) refers to a length from a position of a
critical cross-section 14 of thepin 2 to acritical cross-section 13 of thebox 3. - In addition, the minimum value Lmin (mm) of the screw length L refers to a minimum necessary length of the screw length L defined in the expression (1).
- In addition, as illustrated in
Fig. 1 , the pipe thickness t (mm) of the raw pipe portion refers to a pipe thickness of theunprocessed portion 6 of the pin and the unprocessed portion 7 (raw pipe portion) of the box. The pipe diameter D (mm) of the raw pipe portion refers to a pipe diameter of each of theunprocessed portion 6 of the pin and the unprocessed portion 7 (raw pipe portion) of the box. - Dt (mm) refers to an average screw diameter of the screw valleys in the taper screw which is a shorter effective screw length of either the box or the pin.
- Here, the expression (1) for obtaining the minimum necessary screw length (that is, the minimum value Lmin of the screw length) will be described.
- The joint strength (tensile strength of the screw joint 1) is determined by a portion having a smaller cross-sectional area among respective
critical cross-sections 13 of the box andcritical cross-sections 14 of the pin 2 (seeFig. 1 ). Here, the critical cross-section refers to a cross-section orthogonal to the pipe axis where breakage tends to occur most in a tensile load state of the joint portion. - For example, in a case of the screw joint 1 for the oil well pipe illustrated in
Fig. 1 , as thecritical cross-section 13 of thebox 3, a cross-section located on a load flank surface of a first screw thread in the region of thescrew row 17 on the female screw portion 5 side is adopted. In addition, as thecritical cross-section 14 of thepin 2, a cross-section located on a load flank surface of a second screw thread in the region of thescrew row 17 on the male screw portion 4 side is adopted. Moreover, the load flank surface refers to a flank surface on a side where a load is applied against a tensile force in the pipe axis direction. Therefore, in a case of the joint portion illustrated inFig. 1 , the cross-sectional area of thecritical cross-section 14 of thepin 2 is smaller than the cross-sectional area of thecritical cross-section 13 of thebox 3, so that the joint strength is determined based on thecritical cross-section 14 of thepin 2. - Normally, in a case where the strength (tensile strength of each raw pipe portion of the
pin 2 and the box 3) of the raw pipe is 100%, in the integral joint, since the cross-sectional area of the critical cross-section is necessarily smaller than the cross-sectional area of the raw pipe, the joint strength of the integral joint becomes less than 100% of the strength of the raw pipe. -
-
- The shear stress ratio is set to be equal to or less than a value expressed by ((1/√3)/the joint efficiency), so that the shear fracture can be prevented. From the viewpoint of securing safety, it is preferable that a safety factor 0.8 is applied to the expression (4) (that is, the safety factor 0.8 is multiplied on a right side of the expression (4)), and the shear stress ratio is set to be equal to or less than (0.46/joint efficiency). Moreover, in the present invention, since an upper limit of the screw length is set to Lmin × 2.5 by the expression (2), a lower limit of the shear stress ratio is equal to a case where the safety factor 0.4 is applied and is calculated as (0.23/joint efficiency).
-
-
-
- A condition that satisfies an equal sign of the expression (6) is the minimum length Lmin of L, and the expression (1) is obtained by solving the expression for Lmin.
- Moreover, in the integral joint, as described above, there are some cases in which the regions of the male and female taper screws are divided into two in the pipe axis direction in each of the pin and the box. The present invention can also be applied to the integral joint of such designs.
- As described above, according to the present invention, it is possible to design the screw joint for an oil well pipe to secure the minimum necessary screw length (Lmin) so that the screw portion is not subjected to the shear fracture. Therefore, a processing time for performing threading process or a rolling process in the steel pipe (raw pipe) is decreased (reduced), and a construction time required for tightening the male and female taper screws is also decreased (reduced) . As a result, an excellent design in which the productivity is improved and the manufacturing cost can be reduced is provided, and both the productivity and the shear fracture strength of the joint can be improved.
- The screw length (L (mm)) having an appropriate allowable width while having a screw characteristic normally required can be calculated. Therefore, since the region in the thickness direction occupied by the screw portion in which the screw length (L (mm)) becomes smaller than a general screw length of the related art can be reduced, the thickness of the
nose 15 can be secured and a degree of freedom of the design of the seal can be increased. - Hereinafter, the present invention will be described based on examples. The present invention is not limited to the following examples.
- For a screw joint for an oil well pipe, which includes a pin obtained by machining an end portion of a steel pipe of an outer diameter 9-5/8 inches × thickness 0.545 inches (outer diameter 244.48 mm × thickness 13.84 mm) of a steel type Q125 of API 5CT, and a box corresponding thereto, a pin was prepared by subjecting the end portion to diameter reduction processing at a ratio of 3 to 5%, and cutting the outer diameter side, and a box was prepared by subjecting the end portion to tube expansion at a ratio of 5 to 8%, and cutting the inner diameter side. The number of samples was 6 pairs. The schematic drawing of the screw joint is a semi flush screw joint shown in
Fig 1 . - Using the obtained screw joints for an oil well pipe (test joint Nos. 1 to 6), (1) whether or not the shear fracture occurred, and (2) workability and construction property were respectively evaluated.
- The evaluation whether or not the screw portion of the joint portion was subjected to the shear fracture was performed by determining whether or not the screw portion was subjected to the shear fracture in a case where the tensile load was applied based on the joint efficiency calculated from the critical cross-section. Here, an angle of the load flank as a contact surface of the screw thread was set to -5 degrees and an angle of a stabbing flank was set to 15 degrees.
- In each test joint, a processing time (sec) required for manufacturing the pin and the box, and a tightening time (sec) of the pin and the box were respectively measured. The processing time was taken as a sum of respective required times of the pin and the box. The evaluation of the workability and the construction property was performed by obtaining a ratio to a reference value based on the processing time and the tightening time in the screw joint for the oil well pipe of test joint No. 6 illustrated in Table 1. In a case where the obtained ratio is less than 1.0, it was evaluated that the workability and the construction property were excellent, and in a case where the obtained ratio is 1.0 or more, it was evaluated that the workability and the construction property were inferior. Moreover, test joint No. 6 was designed not to use the screw length L (mm) defined in the present invention but to use a general screw length of the related art.
- The results obtained as described above are illustrated in Table 1.
[Table 1] Test joint No. Box Pin Ratio αt of effective screw length to screw length L Average screw diameter: Dt (mm) Joint efficiency (%) Minimum value of screw length in screw row: Lmin (mm) Screw length in screw row: L (mm) Screw length ratio L/Lmin Evaluation Remarks Pipe thickness of raw pipe portion: tb (mm) Pipe diameter of raw pipe portion: Db (mm) Pipe thickness of raw pipe portion: tp (mm) Pipe diameter of raw pipe portion: Dp (mm) Shear fracture Workability Construction property Processing time (sec) Ratio Tightening time (sec) Ratio 1 13.84 244.48 13.84 244.48 0.6 230.64 70 27.97 30 1.1 No 150 0.75 192 0.91 Example of present invention 2 13.84 244.48 13.84 244.48 0.6 230.64 70 27.97 69 2.5 No 189 0.95 208 0.98 Example of present invention 3 13.84 244.48 13.84 244.48 0.4 230.64 70 41.95 60 1.4 No 180 0.90 204 0.96 Example of present invention 4 13.84 244.48 13.84 244.48 0.6 230.64 70 27.97 100 3.6 No 220 1.10 220 1.04 Comparative example 5 13.84 244.48 13.84 244.48 0.6 230.64 70 27.97 25 0.9 Yes 145 0.73 190 0.90 Comparative example 6 13.84 244.48 13.84 244.48 0.6 230.64 70 27.97 80 2.9 No 200 - 212 - Reference - As illustrated in Table 1, in the examples (test joint Nos. 1 to 3) of the present invention, the screw length L (mm) in the screw rows satisfied the expression (2), so that it was found that the workability and the construction property were excellent. In addition, there was no shear fracture. On the other hand, in a comparative example (test joint No. 4) in which the screw length L exceeds an upper limit value of the expression (2), it was found that the processing time and the tightening time were increased, and the productivity was reduced. In a comparative example (test joint No. 5) in which the screw length L is lower than a minimum value of a lower limit value of the expression (2), it was found that the shear fracture occurred and the strength was insufficient.
- That is, according to the present invention, the screw joint for an oil well pipe having the appropriate screw length L in a range not causing the shear fracture is designed, so that it is possible to obtain the screw joint for an oil well pipe which has no problem of the shear fracture of the screw and in which the workability and the construction time are reduced (that is, excellent in productivity).
-
- 1
- screw joint for oil well pipe
- 2
- pin
- 3
- box
- 4
- male screw portion
- 5
- female screw portion
- 6
- unprocessed portion of pin
- 7
- unprocessed portion of box
- 9
- seal portion on outer peripheral surface side
- 10
- seal portion on inner peripheral surface side
- 11, 12
- shoulder portion
- 13, 14
- critical cross-section
- 15
- nose
- 16
- nose hole
- 17
- screw row
- α
- screw joint axis
Claims (1)
- A screw joint for an oil well pipe of an integral type, comprising:a pin that is provided with a male screw portion which is a male taper screw, at one end of a steel pipe; anda box that is provided with a female screw portion which is a female taper screw fitted to the male screw portion, at one end of the steel pipe,wherein a structure, in which the pin and the box are in metal contact with each other to seal a fluid, is provided at least at one place of a seal portion on an outer peripheral surface side of a pipe end side of the pin and a seal portion on an inner peripheral surface side of a pipe end side of the box,wherein a minimum value Lmin (mm) of a screw length L (mm) in screw rows of the male taper screw and the female taper screw is defined by expression (1), andwherein the screw length L (mm) in the screw rows satisfies expression (2).Here, t: a pipe thickness (mm) of each of raw pipe portions which are unprocessed portions of the box and the pin,D: a pipe diameter (mm) of each of the raw pipe portions which are unprocessed portions of the box and the pin,αt: a ratio of an effective screw length to the screw length L, a shorter effective screw length of the box or the pin being chosen for the effective screw length,Dt: an average screw diameter (mm) of screw valleys in the taper screw having a shorter effective screw length of the box or the pin, andjoint efficiency: tensile strength of the joint portion/tensile strength of the raw pipe portion.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2018038495 | 2018-03-05 | ||
PCT/JP2019/005177 WO2019171899A1 (en) | 2018-03-05 | 2019-02-14 | Screw joint for oil well pipe |
Publications (3)
Publication Number | Publication Date |
---|---|
EP3763981A1 true EP3763981A1 (en) | 2021-01-13 |
EP3763981A4 EP3763981A4 (en) | 2021-03-31 |
EP3763981B1 EP3763981B1 (en) | 2023-01-25 |
Family
ID=67847228
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19764512.0A Active EP3763981B1 (en) | 2018-03-05 | 2019-02-14 | Screw joint for oil well pipe |
Country Status (14)
Country | Link |
---|---|
US (1) | US11549620B2 (en) |
EP (1) | EP3763981B1 (en) |
JP (1) | JP6888677B2 (en) |
CN (1) | CN111868429B (en) |
AR (1) | AR114654A1 (en) |
AU (1) | AU2019230247C1 (en) |
BR (1) | BR112020017885B1 (en) |
CA (1) | CA3088237C (en) |
ES (1) | ES2937962T3 (en) |
MX (1) | MX2020009213A (en) |
RU (1) | RU2742962C1 (en) |
SA (1) | SA520420087B1 (en) |
UA (1) | UA125003C2 (en) |
WO (1) | WO2019171899A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA3113361A1 (en) * | 2020-03-26 | 2021-09-26 | NejiLaw inc. | Oil well pipe connection structure and oil well pipe |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5232475B2 (en) | 1973-08-13 | 1977-08-22 | ||
SU1615315A1 (en) * | 1987-12-08 | 1990-12-23 | Нижнеднепровский Трубопрокатный Завод Им.Карла Либкнехта | Joint of thin-wall casing pipe |
CA1322773C (en) * | 1989-07-28 | 1993-10-05 | Erich F. Klementich | Threaded tubular connection |
US5492375A (en) * | 1994-07-21 | 1996-02-20 | Grant Tfw, Inc. | Drill pipe with improved connectors |
US5687999A (en) | 1995-10-03 | 1997-11-18 | Vallourec Oil & Gas | Threaded joint for tubes |
JPH10318453A (en) * | 1997-05-15 | 1998-12-04 | Nippon Steel Corp | Steel pipe joint structure |
JP3668094B2 (en) * | 2000-04-10 | 2005-07-06 | 新日本製鐵株式会社 | Pipe fitting |
US7431347B2 (en) | 2003-09-24 | 2008-10-07 | Siderca S.A.I.C. | Hollow sucker rod connection with second torque shoulder |
ITRM20050069A1 (en) | 2005-02-17 | 2006-08-18 | Tenaris Connections Ag | THREADED JOINT FOR TUBES PROVIDED WITH SEALING. |
US8246086B2 (en) * | 2008-09-10 | 2012-08-21 | Beverly Watts Ramos | Low cost, high performance pipe connection |
US9885214B2 (en) | 2009-07-14 | 2018-02-06 | Ptech Drilling Tubulars, Llc | Threaded tool joint connection |
JP5849749B2 (en) | 2011-02-28 | 2016-02-03 | Jfeスチール株式会社 | Threaded joints for pipes |
CN103046876A (en) | 2012-12-25 | 2013-04-17 | 江苏和信石油机械有限公司 | Prospection drill rod with ultralarge caliber in 11-1/4 inches |
FR3008763B1 (en) * | 2013-07-18 | 2015-07-31 | Vallourec Mannesmann Oil & Gas | ASSEMBLY FOR THE PRODUCTION OF A THREADED JOINT FOR DRILLING AND OPERATING HYDROCARBON WELLS AND RESULTING THREAD |
JP6390321B2 (en) * | 2013-10-29 | 2018-09-19 | 新日鐵住金株式会社 | Threaded joints for steel pipes |
JP5971264B2 (en) * | 2014-01-10 | 2016-08-17 | Jfeスチール株式会社 | Threaded joint for extra-thick oil well pipe |
CN204703787U (en) * | 2015-01-07 | 2015-10-14 | 中国石油天然气股份有限公司 | Non-standard 346.08mm buttress thread casing joint |
CN108138994B (en) | 2015-10-21 | 2020-01-24 | 日本制铁株式会社 | Threaded joint for steel pipe |
CN106837196A (en) | 2017-02-22 | 2017-06-13 | 西南石油大学 | A kind of ultrahigh anti-torsion tool joint thread suitable for extended reach well |
RU186585U1 (en) * | 2018-08-03 | 2019-01-24 | Общество с ограниченной ответственностью "Пермская компания нефтяного машиностроения" | Double threaded connection |
-
2019
- 2019-02-14 EP EP19764512.0A patent/EP3763981B1/en active Active
- 2019-02-14 MX MX2020009213A patent/MX2020009213A/en unknown
- 2019-02-14 CA CA3088237A patent/CA3088237C/en active Active
- 2019-02-14 BR BR112020017885-3A patent/BR112020017885B1/en active IP Right Grant
- 2019-02-14 WO PCT/JP2019/005177 patent/WO2019171899A1/en unknown
- 2019-02-14 JP JP2019530840A patent/JP6888677B2/en active Active
- 2019-02-14 AU AU2019230247A patent/AU2019230247C1/en active Active
- 2019-02-14 ES ES19764512T patent/ES2937962T3/en active Active
- 2019-02-14 US US16/977,835 patent/US11549620B2/en active Active
- 2019-02-14 RU RU2020129041A patent/RU2742962C1/en active
- 2019-02-14 UA UAA202005668A patent/UA125003C2/en unknown
- 2019-02-14 CN CN201980017424.XA patent/CN111868429B/en active Active
- 2019-03-01 AR ARP190100515A patent/AR114654A1/en active IP Right Grant
-
2020
- 2020-09-03 SA SA520420087A patent/SA520420087B1/en unknown
Also Published As
Publication number | Publication date |
---|---|
BR112020017885B1 (en) | 2023-10-03 |
SA520420087B1 (en) | 2022-10-30 |
EP3763981B1 (en) | 2023-01-25 |
AR114654A1 (en) | 2020-09-30 |
RU2742962C1 (en) | 2021-02-12 |
CN111868429A (en) | 2020-10-30 |
EP3763981A4 (en) | 2021-03-31 |
CN111868429B (en) | 2022-04-15 |
UA125003C2 (en) | 2021-12-22 |
US20210025523A1 (en) | 2021-01-28 |
JPWO2019171899A1 (en) | 2020-04-16 |
JP6888677B2 (en) | 2021-06-16 |
ES2937962T3 (en) | 2023-04-03 |
CA3088237A1 (en) | 2019-09-12 |
AU2019230247A1 (en) | 2020-07-30 |
WO2019171899A1 (en) | 2019-09-12 |
AU2019230247C1 (en) | 2022-10-27 |
MX2020009213A (en) | 2021-01-15 |
BR112020017885A2 (en) | 2020-12-22 |
US11549620B2 (en) | 2023-01-10 |
AU2019230247B2 (en) | 2021-11-11 |
CA3088237C (en) | 2022-11-01 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2002165B1 (en) | Tubular threaded joint | |
EP3486540B1 (en) | Threaded joint for oil well steel pipe | |
AU2016241774B2 (en) | Threaded pipe joint | |
JP5849749B2 (en) | Threaded joints for pipes | |
EP4012239A1 (en) | Threaded coupling for steel pipe | |
EP3763981B1 (en) | Screw joint for oil well pipe | |
JPH06281061A (en) | Threaded joint for oil well | |
EP4083369A1 (en) | Threaded joint for tubes | |
US11353144B2 (en) | Threaded joint | |
WO2021059807A1 (en) | Screw-threaded joint | |
EP2937612B1 (en) | Threaded joint for pipe | |
EP3842680A1 (en) | Threaded joint for steel pipes |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE |
|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20200731 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
A4 | Supplementary search report drawn up and despatched |
Effective date: 20210226 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F16L 15/04 20060101AFI20210222BHEP Ipc: E21B 17/042 20060101ALI20210222BHEP |
|
DAV | Request for validation of the european patent (deleted) | ||
DAX | Request for extension of the european patent (deleted) | ||
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20220817 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1546124 Country of ref document: AT Kind code of ref document: T Effective date: 20230215 Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602019024831 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: FP |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 20230222 Year of fee payment: 5 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2937962 Country of ref document: ES Kind code of ref document: T3 Effective date: 20230403 |
|
REG | Reference to a national code |
Ref country code: NO Ref legal event code: T2 Effective date: 20230125 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NO Payment date: 20230222 Year of fee payment: 5 Ref country code: FR Payment date: 20230310 Year of fee payment: 5 Ref country code: ES Payment date: 20230301 Year of fee payment: 5 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG9D |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20230222 Year of fee payment: 5 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 1546124 Country of ref document: AT Kind code of ref document: T Effective date: 20230125 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230525 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230525 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230426 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20230228 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602019024831 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230214 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230228 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230228 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20230629 Year of fee payment: 5 Ref country code: GB Payment date: 20230407 Year of fee payment: 5 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
26N | No opposition filed |
Effective date: 20231026 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20230125 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230214 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230228 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 20240108 Year of fee payment: 6 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20240304 Year of fee payment: 6 |